Grinding machine



Maly 2o, 1941.

V. W.'GIDEON GRINDING' MACHINE Filed Jan. 24, 1940 4 Sheets-Sheet 1 May 20, v .1941. v. w. Giur-:0N

A GRINDING MACHINE Filed Jan. 24, 1940 4 Sheets-Sheet 2 V. W. GIDEON GRINDING MACHINE May 20, 1941.

Filed Jan. 24, 1940 4 Sheets-Sheet. 3

May 20,' 1941- v. w. GIDEoN 4 2,242,781

GRINDING MACHINE Filed Jan. 24, 1940 4 Sheets-Sheet 4 Patented May 20, 12941 UNITED s'm'rlezs' PATENT OFFICE GBINDING MACHINE Victor W. Gideon, Chicago, IIL, assigner to Boyar- Schnltz Corporation, Chicago, lll., a corporation of Illinois Application January ai, 1940, serial No. 315,366 3 claims. (c1. 51-34) ciprocatory spindle movements from a common source of power.

Another object is to provide a new and improved spindle assembly for a grinding machine which embodies means for axially reciprocating the spindle including cooperating cam members and a common means for driving one of the cooperating cam members at spindle speed and the other cooperating cam member at a predeter.

mined speed other than spindle speed.

Another object is to provide in a grinding machine a novel over-arm assembly in which an,

axially reciprocatory, vertically disposed, grindp ing element spindle is supported for angular, radial or straight line adjustments and is arranged to be driven and reciprocated by a source of power that may, as desired, be a part of the assembly or the driving means of another tool.

Another object is to provide a novel over-arm assembly of the character above set forth which is adapted for operative association, either as an attachment to or as an integral part of, a grinding machine having a vertical spindle supporting a grinding element at its upper end.

Other objects and advantages will become ap-4 parent in the following description and from the accompanying drawings, in which:

Figure 1 shows in front elevation the operative structure of a grinding machine embodying the features of the invention.

Fig. 2 is an axial sectional view taken axially of the spindle on the over-arm assembly as indlcated by the line 2-2 of Fig, 3.

Fig. 3 is a plan view of the grinding machine as shown in Fig. 1.

Fig. 4 is a sectional view taken axially of the drive shaft of the over-arm assembly as indicated by the line 4 4 of Fig. 3.

Fig. 5 is a similar view showing the construction as modied to include the prime mover as a part of the over-arm assembly,

Fig. 6 is a view of a detail of the over-arm spindle looking in the direction indicated by the line 6-6 in Fig. 2.

Fig. 7 is a sectional view through the over-arm spindle taken along the line 1-1 of Fig.v 2.

Fig. 8 is a transverse sectional view through the over-arm assembly taken of Fig. 2.

Fig. 9 is a side view of the upper portion of the grinding machine looking from the left-hand side of lthe machine as shown in Fig. 1.

While the invention is susceptible of various modications and alternative constructions, AI have shown in the drawings and will herein describe in detail the preferred embodiments, but it is to be understood that I do not thereby inalong the line 8--8 tend to limit the invention to the specific form disclosed, but intend to cover all modiications and alternative constructions falling within the spirit and' scope of the invention as expressed in the appended claims.

In the following discussion of the present invention, it will be considered in its association with a grinding machine which has a vertically disposed driven spindle arranged to carry a grinding element or the like at its upper end for operation on a superimposed work piece.such as a die, or the like, mounted on a work supporting table. The over-arm assembly may, as will hereinafter more clearly appear, be a permanent part* of the machine structure, or, since it is substan-i tially a unitary assembly, it; may be arrangedV for attachment to an existing machine.

Since the exemplary form of the grinding machine on which, as shown in Fig. 1, the over-arm assembly is mounted is but illustrative of a suitable supporting means for the over-arm assembly and source of power for the assembly spindle, the structural details of the machine will be only briey described, Thus, the grinding machine embodies an upright pedestal I5 having a hollow upper portion I6 traversed by an intermediate wall |65. Below the wall a driving motor Il is supported for transverse adjustment by rods I8. The armature axis of the motor is vertically disposed-and carries a pulley I9 below and adjacent to the wall. A spindle 20 is journaled in the top of the upper portion I6 and carries a pulley 2I at its lower end beneath the wall An idler pulley 22 (Fig. 3) is disposed in the v plane of the pulleys I9 and 2l. A belt 23 passes about the pulleysIS and 22 and one run passesA across the spindle pulley 2i to' drive the spindle 20 at a comparatively high rate of speed. 'I'he idler ulley assembly includes an antifriction roller 4 (Fig. l) having motion through a. circular path derived,`through a worm and worm wheel connection' (not shown), from the idler pulley 22, and this antifnction element coacts' with a plate 25 to impart vertical reciprocatory motion thereto. The plate is a part of a spindle l -ways 3| on the sides of the pedestal.

supporting sleeve assembly 26 which is relatively rotatable to and axially movable with 4the spinof an eccentric finger engageable with the plate 25 by manipulation of a shaft 21 having an operating lever 28. This arrangement serves as a clutch for controlling axial reciprocation of the spindle independently of spindle rotation.

work table 29 is supported above the pedestal by transversely spaced slides 30 mounted in Movement of the table upwardly and downwardly is manually controlled by such means as a hand lever 32 acting through a rock shaft 33 and links 34,- 35 to move the slides 38 vertically. A spring counterbalance 36 acts on the rock shaft to urge the table toward its elevated position. Arcuate ways extendingl transversely of the slides support the table and permit it to be fixed by a locking device 31 in a horizontal or tilted position.

'I'he upper'end 38 of the spindle 20 is normally located beneath the table 29 and is adapted interchangeably to receive a tool chuck or a driving pulley, the latter being herein illustrated and designated 39. When such a tool as a grinding element is secured to the spindle, the machine is adapted for operation on a work piece supported by the table. Replacement of the tool chuck by the pulley 39, and disengagement of the means for vertically reciprocating the spindle, converts the machine to a driving means or prime mover for the spindle of the over-arm assembly.

In a preferred form, the over-arm assembly-includes a vertical tubular standard 48 having at its lower -end a split sleeve 4| disposed on a horizontal axis and provided with clamping screws 42. A cylindrical stud 43 fitting snugly in the sleeve projects horizontally from a plate 44 which is adapted to be secured in any suitable manner to a selected supporting means. In this instance, the plate 44 is secured by screws 45 to the rear side of the upper portion |6 of the pedestal. The sleeve is preferably keyed, as at 46, to the stud 43 for axial but non-rotative adjustment.

The upper end of the standard 4U is open to receive the depending cylindrical arm 41 of an L-shaped casing 48 (Fig. 4). 'Ihe external diameter of the arm 41 is less than the internal diameter of the standard 48 and a sleeve 49 is interposed in the clearance therebetween with its upper end in abutment with a shoulder 50 on the casing. Vertical adjustment of the casing 48 is, in this instance, effected by vertical movement of the interposed sleeve. Thus, the sleeve has an external longitudinally extending rack formed thereon or secured thereto -for engagement by a pinion 52 on a shaft 53 journaled at opposite ends on a semicylindrical projection 54 on thestandard 40. The shaft 53 carries a hand wheel 55. The casing 48, through the arm 41, is rotatably adjustable with respect to the standard 48 and sleeve 49 and its position may besuitably xed as by a set screw device 56 (Fig. 3) mounted on the standard 40 and extending through a slot 51 (Fig. 4) in the sleeve 49 into binding engagement with the externalsurface of the arm 41. The set screw device also maintains the casing in its position of vertical adjustment. If desired, askirt 48a may be secured towthe casing 48 in encircling relation to the upend' of the standard 48.

A drive shaft 58 for the over-arm lspindle extends vertically and axially through and beyond the opposite ends of the arm 41 and is rotatably supported by upper and lower roller bearings 59. The lower end of the shaft 58 has an elongated pulley 50 fixed thereto and a belt 6| running about the pulley 60 and the pulley 39 (Fig. 1) on 4.the grinding machine constitutes the driving connection between the prime mover and the drive shaft of the over-arm assembly. The standard and the sleeve 49 are cut away, as indicated at 62, to admit the belt 6| to the pulley 68.

The upper end of the shaft 58 extends into the corner space of the L-shaped casing 48 and has secured thereto a. pulley 63 having upper and lower belt-receiving grooves 64 and 65 respectively. The pulley is substantially centrally disposed with respect to the cylindrical horizontal arm 66 of the casing 48.

The head of the over-arm assembly in which the over-arm spindle is mounted is supported by the horizontal arm 66. With particular reference to Fig. 2, the head includes a housing having an enlarged cylindrical sleeve section 61 adapted to t snugly within the arm 66 and an integral tubular section 6 8, the axis of which is perpendicular to the axis of the section 61. The section 68 carries the spindle assembly.

The spindle assembly includes a spindle 69 enclosed within an encircling sleeve 10. Near its lower end the sleeve has an annular flange 1| against the outer face of which the inner race 12 of a ball bearing 13 is seated. A ring 14 having a screw -threaded engagement with the end of the sleeve, which is fixed by a set screw 15, binds the inner race against the flange. Near its upper end the sleeve 18 is slightly restricted, as at 16, to receive the inner race 11 of a combined thrust and radial bearing 18. Outer races 19 and of the bearings 13, 18 respectively -arenseated in end collars 8|, 82 formed integrally at the ends of a spindle frame 83.

The frame 83 is adapted to fit snugly within Athe tubular section 68 of the head housing and is secured therein by an upper cap 84 which is secured, as by screws 85, to the upper collar 82 and by screws 86 to the tubular section 68. Removal of the screws 86 permits the spindle assembly and frame 83 to be withdrawn as a unit from the tubular section 68. The cap has an inwardly directed flange 81 for abutment with the outer side of the bearing race 80 to bind it against an oil sealing plate 88 seated on a shoulder 89 on the upper collar 82. In the lower collar 8|, a sealing plate 90 is interposed between the outer race 19 of the bearing 13 and a shoulder 9| on the collar, and such means as a pin 82 prevents relative rotation between the plate and the collar. An oil seal 93 has screw threaded engagement with the collar for engagement with the outer side of the outer race.

The spindle 69 is axially adjustable with respect to the encircling sleeve 10. Thus, the upper end of the spindle has an end bore 94 through which a stem 95 extends into axial screw threaded engagement with the spindle. The uppersend of the sleeve is closed by a plug 96 anday/spring 91, seated in the spindle bore 94, iscompressed between the spindle 4and the plug.

The outer end of the stem extends through the.

cap and is screw threaded, as at 98, for engagement by an elongated nut V99, the inner end of which seats against the plug 96. Hence, the position of the nut on the stem 95 will determine the axial relationship between the spindle andthe encircling sleeve. A set screw device, generally indicated at |00, maintains the relationship between Ithe spindle and sleeve. l

The spindle frame 83, as may be seen clearly from Fig. 2, has an enlarged strengthening ri-b which is elongated in the direction of the spindle axis, is relatively narrow and, as shown in Fig. 8, is of substantial thickness radially. Since the rib, in assembly, extends somewhat into the sleeve section 61, said section and the tubular section 68 at the top of the assembly have a continuing slot |02 providing clearance for the insertion of the spindle support 83 into the tubular section 6B. Oppositely located clearance slots |03 are also formed in the lower portions of the head sections.

Adjoining the upper collar 82, the sleeve has a pulley |04 keyed, as at |05, thereto. Spaced between the pulley |04 and the lower collar 8| is a second narrower pulley |06 supported for rotation relative to the sleeve 10 by an assembly |01 of elongated roller elements. A ring |08 on the sleeve 10 is seated against the inner face` of the flange 1| and a thrust bearing |09 is interposed between the ring and the adjacent side face of the pulley |06. The opposite side face of the pulley |06 is fashioned to provide a cam surface having, in this instance, diametrically opposed low points ||0 and high points The cam is engaged by cam followers herein shown as being antifriction rollers ||2 mounted on the opposite' ends of a shaft ||3 which is held by'a set screw il4, or the like, against axial movement in a diametrical bore ||5 in the spindle 69. The shaft extends through slots ||6 in the sleeve 10, thereby providing the driving connection between the shaft and sleeve, and the slots ||6 are elongated in an axial direction to permit the spindle 69 and shaft I3 to reciprocate axially relative thereto as the antifriction rollers follow the cam surfaces I0, The force exerted on the spindle by the spring 91 maintains -the antifriction rollers against the cam surfaces.

The pulley |04 is driven by a belt ||1 engaging the pulley receiving groove 64 0f the pulley 63 on the drive shaft 58. The pulley |06 is driven by a belt ||8 engaging the pulley groove 65 in the pulley 63. In the present instance, the pulley grooves 64 and 65 have the same eiective diameters so that the belts ||1 and ||8 are driven at the same rates of speed. The pulleys |04 and |06, however, are of different eective diameters, in this instance the pulley |06 having slightly the larger diameter. As a result, the spindle driving pulley |04 will travel at a slightly faster rate of .speed than the pulley |06, causing the cam foilowing roller elements ||2 to advance in the direction of rotation over the slower moving cam Vsurfaces ||0, The speed dierential is predetermined to produce the desired number of axial reciprocations of the spindle with respect to the velocity of spindle rotation and it will be evident that this ratio may be conveniently achieved and maintained by the present construction. While the pulley |06 has been illustrated as being larger than the pulley |04, axial reciprocation would be obtained if it vwere of smaller diameter. Moreover, the speed differ-Y ential could be obtained by making the diameters of the pulley grooves 64 and 65 unequal.

Lubrication to the assembly of the lower bear- Ying 13 may be provided by an oil cup I I9 mounted YYon the cap 84 and communicating with the lower frame 83 and a port |2I in the plate 90. Excess or waste lubrication may drain from the bearing into a receiving groove |22 in the oil seal 93 and thence to exhaust through a port |23 and communicating passages |24 in a fitting |25 on the end collar 8|.

Preferably, through the connection between the cylindrical sleeve section 61 of the head housing and the horizontal arm 664 of the supporting standard assembly, the spindle is relatively adjustable longitudinally and rotatably with respect to the axis of the horizontal arm. As shown, the end of the arm is slotted inwardly, as indicated at |26, and a clamping screw |21 is provided to draw the split sleeve into secure clamping engagement with the sleeve section 61. This sleeve section has a vlongitudinally extending groove |26 releasably engageable by a key |29 seated in a i boss |30 on the arm 66. The. key is retractable out of engagement with the gr'oove |28 by manipulation of a headed stem |3| against the force of a key-seating spring |32 bearing between the key and a closure |33 for the outer end of the boss. The key |29 is itself keyed, as at |34, against rotative movement relative to the boss.

The relationship between the groove |28 and key |29 preferably determines a. zero position of the spindle 69, whichposition will normally be bearing through a passageway |20 in the spindle 75 one in which the spindle axis is vertical. Longitudinal adjustment of the head assembly is obtained by loosening the clamping screw |21 and shifting the head assembly with respect to the supporting arm as desired. For rotational adjustment, the clamping screw is loosened and the key 29 is retracted to permit the head assembly to be rotated about the axis of the supporting arm as shown in dotted outline in Fig. 9. The extent of such adjustment may be conveniently indicated by such means as an indicator ring |35 seated on the cylindrical section B'lA adjacent the end of the arm 66 and having a key pin |36 engaging the groove |20. Suitable cooperating indicia |31 (Fig. 1) may be provided on the ring and arm'.

If desired, the entire area occupied by the pulleys |04 and |06, belts ||1 and H0, and pulley 63 may be ventilated by apertures |36 and |39 in the supporting structures adjoining the'pulleys. Preferably, at least the aperture |39 adjacent the spindle pulleys is screened as at |04.

The structure shown in Fig. 5 is a modification of the over-arm assembly in which the drive shaft is driven by a prime mover combined as a unitary part of the over-arm assembly. Fig. 5 is a sectional view through the lower section of the tubular standard 40, and the portions of the assembly which are not illustrated in this figure are constructed in the manner previously described. In the modified form, the lower end of the standard 40 is somewhat enlarged, as indicated at |4I, and is adapted to beI suitably secured to an appropriate supporting member |42 by such means as a horizontally extending flange |63. Within the enlargement |4| is a transverse wall |44 having an annular offset terminating in a tubular boss |45 substantially coaxial with the drive shaft 58.

The lower end of the drive shaft is vertically splined, as at |46, for engagement with internal splines on a sleeve |41 fixed to the upper end of a stub shaft |40 which is journaled by spaced bearings |49 on the boss |45. An oil cup .|50 supplies lubricant through a tube |5| to the bearings. Below the wall |44 the stub shaft |48 carries a gear |52 engaging an internal ring gear |53 rigid with the armature |54 of a driving mo- A tor |55. The motor is secured to the lower end of the standard through a bracket |56. The modified construction enables the use of the present invention in environments where no existing prime mover is available as a sourceof power for the 'over-arm assembly drive shaft.

From the foregoing, it will be evident that the invention embodies numerous important features and advantages. The connection between the standard 40 and the supporting stud 43 enables i the spindle to be initially located in approximately a desired position with respect to the work supporting table. The arrangement of the arm 41 on the head supporting casing 48, with respect to the standard 40, permits the head to be conveniently adjusted vertically with respect to the work and radially about the axis of the standard 4I as a center. The adjustments of the head longitudinally of the axis of the horizontal arm of the supporting casing, as well as radially of said'axis, venables the 'spindle to be precisely disposed Vfor proper engagement with the work. lThe head assembly for supporting the spindle is comparatively simple and the assembly as a Whole is convenient to install. Furthermore, the improved meansby which the spindle is driven rotatably .and reciprocably at different rates of speed from ing a section depending into engagement with said support and rotatably adjustable with respect thereto, means for vertically adjusting said member relative to said support, a spindle, a spindle supporting head, means for mounting said head on said member with the axis of said spindie disposed substantially vertically including means for adjustably moving said head toward and away from said support and for rotatably adjusting said head-about a horizontal axis, and means for driving said spindle.

2. In a grinding machine of the character described,l the combination of a vertical support, means for securing said support to a stationary base part including means for adjusting said support relative to said base part, a member having a section depending into said support, a sleeve interposed between said support and said section for rotatably supporting .said member, means for vertically translating said sleeve to adjust said member relative to said support, a spindle, means for mounting said spindle on said member with the axis of said spindle disposed substantially vertically, and means for driving said -spindle.

3. In a grinding machine of the character described, the combination of a tubular vertical support, a horizontal member having a tubular secvtion depending into said support and rotatable relativeV thereto, interposed means for vertically l moving said member, a spindle, a spindlesupporting head, hollow means for mounting said head on said member, and spindle driving means extending through said support, section and hollow means.

VICTOR W. GIDEON 

